JP4928513B2 - Torsional vibration reduction device - Google Patents

Description

  The present invention relates to a torsional vibration reducing device, which improves the strength of a holding member that holds a spring.

  A torsional vibration reducing device is provided between the crankshaft of the engine mounted on the vehicle and the turbine of the torque converter. The torsional vibration reducing device elastically connects an input side member connected to an engine crankshaft, an output side member connected to a turbine of a torque converter, and the input side member and the output side member in a rotational direction. The springs are connected and arranged along the circumferential direction, and a holding member that restricts the springs in the radial direction and the axial direction.

There exists a thing of patent document 1 as a conventional torsional vibration reduction apparatus. This torsional vibration reducing device is disposed along the circumferential direction between a drive plate 72 coupled to the piston 71, a driven plate 73 facing the drive plate 72, and between the drive plate 72 and the driven plate 73. A torsion spring 74 and a spring holder 75 for preventing the torsion spring 74 from rubbing against the driven plate 73 and the drive plate 72 to generate hysteresis.
JP 2002-48217 A

  However, the spring holder 75 is configured to support the entire weight of the torsion spring 74. In particular, when the torsion spring 74 is compressed and the driven plate 73 and the drive plate 72 are rotated relative to each other and twisted in the rotational direction, the spring When a large stress is generated in the torque transmission portion 75d of the holder 75 and the torsional vibration reduction device must increase the weight of the torsion spring 74 to cope with high torque, the stress generated in the torque transmission portion 75d is increased. It is becoming an obstacle to ensure the durability of parts. Further, in order to simultaneously compress the pair of torsion springs 74 in a balanced manner, the inertia weight in the rotational direction of the spring holder 75 must be made as small as possible. For this reason, the spring holder 75 is desired to be lightened as much as possible. There exists a problem that the intensity | strength of the spring holder 75 falls.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a torsional vibration reducing device that improves the strength of a spring holder.

The invention according to claim 1 is an input side member connected to a crankshaft of an engine via a piston, an output side member provided opposite to the input side member and connected to a transmission, and the input side member; At least one pair of springs arranged along the circumferential direction between the output side member and compressed between the input side member and the output side member and comprising a pair of spring members; and an outer periphery of the spring In the torsional vibration reduction device having an annular portion that surrounds the side and a holding member that protrudes from the annular portion toward the inner peripheral side and is interposed between the pair of spring members, the circle of the coupling portion When the circumferential length is W and the radial length from the base end portion of the connecting portion to the distal end portion on the center side is S, W> S is set, and the intermediate portion in the circumferential direction of the connecting portion is set. the inner peripheral side of the position, weight notch is formed And wherein the door.

According to the present invention, if the length in the circumferential direction of the connecting portion is W and the length in the radial direction from the base end portion of the connecting portion to the distal end portion on the center side is S, W> S is set. because there, will be annular portion by the connecting portion have the long is reinforced, even when the weight of the spring is increased by the design, it can be suppressed the stress generated during the rotation.
In addition, since the lighter cutout portion is formed on the inner peripheral side of the connecting portion in the holding member, the inertia of the torsional vibration reducing device is reduced. In addition, since the connecting portion is away from the axial center position, the influence of the self-weight centrifugal force can be largely suppressed even if the amount of the lighter cutout portion is small.

The invention according to claim 2, in torsional vibration reducing device according to claim 1, wherein the connecting portion, the cross-sectional shape when taken along a cross section passing through the axis of the holding member, a plate-shaped portion of the spring It is formed in the shape wound along the strand.

  According to the present invention, the connecting portion of the holding member is formed in a shape in which the cross-sectional shape when cut along the cross section passing through the axial center is formed by winding the plate-like portion along the element wire of the spring. Large area to receive the end face.

According to the torsional vibration reduction device according to claim 1, when the circumferential length of the connecting portion is W, and the radial length from the proximal end portion of the connecting portion to the distal end portion on the center side is S, Since W> S is set , the annular portion is reinforced by the long connecting portion, and even when the weight of the spring is increased by design, the stress generated during the rotation can be suppressed.
In addition, since the lighter cutout portion is formed on the inner peripheral side of the connecting portion in the holding member, the inertia of the torsional vibration reducing device is reduced. In addition, since the connecting portion is away from the axial center position, the influence of the self-weight centrifugal force can be largely suppressed even if the amount of the lighter cutout portion is small.

According to the torsional vibration reduction device according to claim 2 , the connecting portion of the holding member is formed in a shape in which a cross-sectional shape when cut by a cross-section passing through the shaft center is formed by winding a plate-like portion along a spring wire. Therefore, the area for receiving the end face of the spring is large. Accordingly, the end face of the spring can be stably supported, and a retainer need not be provided.

Embodiments of a torsional vibration reducing device according to the present invention will be described below.
(Constitution)
A torque converter is connected between the crankshaft of the engine and the transmission, and the torque converter is provided with a torsional vibration reducing device 1 shown in FIG.

  More specifically, the engine crankshaft is located on the left side of FIG. 1A, and a front cover (not shown) as a cover is coupled to the end of the crankshaft. The front cover is provided with a lockup piston 2 as a piston that can be connected and disconnected by moving in the axial direction, and the torsional vibration reducing device 1 is connected to the lockup piston 2.

  The torsional vibration reducing device 1 includes an input side member 3 coupled to the lock-up piston 2 and a torque converter (not shown) which is provided opposite to the input side member 3 and located on the right side of FIG. And an output side member 4 connected to the transmission via a turbine. In addition, about 1/4 at the upper right of FIG.1 (b) is a figure of the state in which the output side member 4 exists, and the other part is a figure by which the output side member 4 is abbreviate | omitted.

  The lock-up piston 2 has a hole 2a formed in the center thereof, and a friction lining 2b is coupled to the surface near the outer peripheral surface and facing the front cover. Due to the presence of the friction lining 2b, the lock-up piston 2 moves to the left in the axial direction, frictionally couples with the front cover, and rotates integrally with the front cover. A cylindrical cylindrical portion 2 c is formed on the outer peripheral portion of the lockup piston 2.

  The input side member 3 is coupled to the transmission side surface of the lockup piston 2. That is, as shown in FIG. 2 (b), the input side member 3 has a large hole 3e formed at the center portion and an insertion hole 3h formed outside the hole 3e, which is inserted through the insertion hole 3h. The input side member 3 is coupled to the lockup piston 2 via a rivet 7.

  When the input side member 3 is coupled to the lockup piston 2 via the rivet 7, the input side member 3 is rotated in the circumferential direction with respect to the lockup piston 2 so that the insertion holes of the rivet 7 are aligned. There is a need. In this state of alignment, it is necessary to prevent the orifice 2d formed in the lockup piston 2 from being blocked by the input side member 3. The orifice 2d is formed from the pressure chamber on the right side of the lock-up piston 2 in FIG. 1A that presses the lock-up piston 2 even when the lock-up piston 2 is coupled to the front cover by lock-up. 2 is provided to allow hydraulic oil to flow to the left side of 2. In order to prevent the orifice 2d from being blocked by the input side member 3, the input side member 3 is formed with a long elongated hole 3m in the circumferential direction outside the slit 3d, and the slit 3d and the slit 3d in the circumferential direction are formed. A recess 3n is formed on the inner peripheral surface of the hole 3e. For this reason, when the positions in the circumferential direction of the insertion hole of the lockup piston 2 and the insertion hole 3h of the input side member 3 are matched, the position of the orifice 2d of the lockup piston 2 is the long hole 3m of the input side member 3. Alternatively, the orifice 2d is not blocked by the input side member 3 in correspondence with the position of the recess 3n.

  The coupling between the lock-up piston 2 and the input side member 3 is not limited to a rivet. For example, the lock-up piston 2 is embossed to form a convex portion, and the convex portion is formed in the insertion hole 3h formed in the input side member 3. It may be inserted and caulked or press-fitted. Since this input side member 3 compresses the 1st spring 11 and the 2nd spring 12 which are mentioned later, or slides with the 1st spring 11 and the 2nd spring 12 and the holding member 6 which is mentioned later, high strength and hardness And carbonitriding or the like is performed.

  As shown in FIG. 3, the output side member 4 is formed with a large hole 4e in the center, and a mounting hole 4f for connecting the output side member 4 to the turbine of the torque converter is formed in the vicinity of the hole 4e. Has been.

  A spring is provided along the circumferential direction between the input side member 3 and the output side member 4 which are provided so as to face each other, and the input side member 3 and the output side member 4 are connected by the spring. Are elastically coupled in the rotational direction. As the spring, there are a first spring 11 provided on the outer peripheral side and a relatively short second spring 12 provided on the inner peripheral side. In order to form a spring accommodating space for accommodating the first spring 11 and the second spring 12, the input side member 3 and the output side member 4 are provided with a pair of spring receiving portions. Details will be described below.

  First, the spring receiving part of the input side member 3 will be described. As shown in FIG. 2 (b), on the outer peripheral side of the input side member 3, in order to form a spring accommodating space for accommodating the first spring 11, the first input side spring receiving portions 3a are respectively along the circumferential direction. In this embodiment, four pairs are provided. That is, it is configured as follows. As shown in FIG. 2B, four protrusions 3c protruding outward in the radial direction are formed on the outer peripheral side of the input side member 3 at substantially equal intervals along the circumferential direction. As shown in FIG. 2A, the cross-sectional shape of the protrusion 3c is wound along the winding direction of the first spring 11 in order to secure an area for receiving the end face of the first spring 11. It is formed in a letter shape. An arc-shaped throttle portion 3j is formed on the radially inner side of the protrusion 3c for the purpose of reinforcement. Both ends of the protrusion 3c in the circumferential direction are the first input-side spring receivers 3a back to back, and a space between the protrusions 3c in the circumferential direction is a spring accommodating space. The first input-side spring receiving portion 3a is disposed on the inner side in the radial direction of an annular portion 6e of the holding member 6 described later. In order to restrict the inner peripheral side and the axial transmission side of the first spring 11 accommodated in the spring accommodating space, a spring restricting portion is provided on the outer peripheral side of the input side member 3 as shown in the lower part of FIG. 3 g is formed in an arc shape along the circumferential direction.

  On the other hand, on the inner peripheral side of the input side member 3, in order to form a spring accommodating space for accommodating the second spring 12, four pairs of second input side spring receiving portions 3b are provided along the circumferential direction. ing. That is, it is as follows. Four substantially rectangular slits 3d are formed on the inner peripheral side of the input side member 3, and both sides in the circumferential direction of the slit 3d are formed in a "<" shape as shown in the lower part of FIG. A second input side spring receiving portion 3b that is bent and is paired is formed. A spring accommodating space is formed between the second input side spring receiving portions 3b. Further, on the inner peripheral side and the outer peripheral side of the slit 3d, as shown in the lower part of FIG. 2A, the spring is bent to the right to restrict the inner and outer peripheral sides of the second spring 12 and the axial transmission side. The part 3i is formed along the circumferential direction. The engine side of the second spring 12 is regulated by the lockup piston 2.

  The first input side spring receiving portion 3a and the second input side spring receiving portion 3b are arranged at positions farthest along the circumferential direction, and as shown in FIG. An insertion hole 3h for inserting the rivet 7 is disposed in an intermediate portion between the first input side spring receiving portion 3a and the second input side spring receiving portion 3b.

Next, a first output side spring receiving portion 4a that forms a spring accommodating space for accommodating the first spring 11 is accommodated on the outer peripheral side of the output side member 4, and the second spring 12 is accommodated on the inner peripheral side. Four pairs of second output-side spring receiving portions 4b that form spring accommodating spaces are provided along the circumferential direction. As shown in FIG. 3, four projections 4c projecting in the axial direction are formed on the outer peripheral side of the output side member 4 along the circumferential direction, and the projections 4c are back-to-back at both ends in the circumferential direction. A first output side spring receiving portion 4a is provided. A spring accommodating space for the first spring 11 is formed between the protrusions 4c.
Further, on the inner peripheral side of the output side member 4, protrusions 4d projecting in the same direction as the first output side spring receiving part 4a are formed by cutting and raising, and at both ends in the circumferential direction of the projection part 4d. A pair of second output side spring receiving portions 4b is formed, and a spring accommodating space for the second spring 12 is formed between the projections 4d in the circumferential direction. As shown in FIG. 1 (b), a gap is formed by an angle θ along the circumferential direction between the second input side spring receiving portion 3b and the second output side spring receiving portion 4b. When the input side member 3 and the output side member 4 are relatively rotated by the angle θ, the compression of the second spring 12 is started.

  The protrusions 4c and 4d protrude toward the axial engine side as shown in the upper part of FIG. 3A, and as shown in FIG. 1A, the output side member 4 is connected to the input side member 3 from the transmission side. Built towards the. For this reason, in a state where the first spring 11 and the second spring 12 are held in the two spring accommodating spaces on the outer side and the inner side of the input side member 3, the protruding portions 4c and 4d can be inserted and assembled in the axial direction. .

  Between the protrusions 4c in the circumferential direction of the output side member 4, as shown in the lower part of FIG. 3A, a spring restricting portion for restricting the radially inner side of the first spring 11 and the axial transmission side. 4 g is formed along the circumferential direction so as to correspond to the spring restricting portion 3 g of the input side member 3.

  A first spring 11 is provided between the pair of first input side spring receiving portions 3a and between the pair of first output side spring receiving portions 4a. A second spring 12 is provided between the two input side spring receiving portions 3b and between the second output side spring receiving portions 4b. The first spring 11 is configured by connecting a pair of split springs 11a, and the first spring 11 and the first input side spring receiving portion are configured so that the pressing of both ends of the first spring 11 is stably performed. A retainer 8 is provided between 3a.

  A holding member 6 that restricts the radially outer side and both axial sides of the first spring 11 is provided. The holding member 6 includes an annular portion 6e that surrounds the outer peripheral side of the first spring 11, and four connecting portions 6c that protrude from the annular portion 6e to the inner peripheral side and are interposed between the pair of split springs 11a. The holding member 6 is configured to be rotatable relative to the input side member 3 and the output side member 4. The holding member 6 alone holds the first spring 11, and the held first spring 11 hardly rubs against any of the input side member 3 and the output side member 4 during normal operation. Since excessive hysteresis does not occur, the function as a damper is improved.

  A pair of inner protrusions 6a and 6b that restrict the first spring 11 from moving in the axial direction are formed at both ends of the annular portion 6e. The ring portion 6e has a necessary minimum strength that can hold the first spring 11 without rubbing against other members at a rotational speed (1000 to 2500 rpm) that must function as a damper for a countermeasure against a booming noise. It is necessary to keep it. In the case of the present embodiment, basically, the first spring 11 is set to be supported by the annular portion 6e of the holding member 6. However, in some cases, the strength of the annular portion 6e is intended to reduce the weight. Therefore, even if the annular portion 6e is deformed by the centrifugal force generated in the first spring 11 at a rotation speed of more than 3000 rpm with a certain margin, for example, the annular portion 6e is locked. You may make it support indirectly by the said cylindrical part 2c of the up piston 2. FIG.

  The connecting portion 6c is for connecting the pair of split springs 11a in the circumferential direction, and the cross-sectional shape when cut along a cross section passing through the axis is the plate-like portion as the element wire of the first spring 11. It is formed in a shape wound along. That is, as shown in the lower part of FIG. 4A, the connecting portion 6c is wound inward in correspondence with the winding shape of the first spring 11 and has a substantially “C” shape. The connecting portion 6c has a circumferential length set to a predetermined value W. As shown in FIG. 4B, the predetermined width W is a length in the radial direction from the base end portion, which is a boundary portion with the annular portion 6e of the connecting portion 6c, to the distal end portion on the center side. Then, W> S is set longer. Since the connecting portion 6c has a substantially “C” shape and the contact area with the end surface of the first spring 11 is increased, the retainer 8 is provided at the end of the split spring 11a and the portion that contacts the connecting portion 6c of the holding member 6. Is not provided. This is because the connecting portion 6c has a sufficiently large contact area with the split spring 11a, and the end portion of the split spring 11a is stably supported. And the slit 6d is formed in the inner peripheral side of the connection part 6c along the axial direction as a weight reduction notch part. The slit 6d is formed at a substantially intermediate position of the length W in the circumferential direction. The slit 6d can be used for positioning in the assembly process.

  The holding member 6 configured as described above is manufactured by drawing a flat plate into a ring shape and drawing it. Since the holding member 6 contacts and slides on the first spring 11 on which centrifugal force acts, high strength and durability are required, and carbonitriding is performed. A portion that slides with the first spring 11 may be provided with a lubricating coating.

The projection 3c formed on both sides of the spring receiving portion 3a of the input side member 3 constitutes an inner guide portion 3k that regulates the inner peripheral side of the annular portion 6e. An outer protrusion 3f is formed that extends from the transmission side to the outside in the radial direction and restricts the annular portion 6e from moving to the transmission side. On the other hand, the engine-side restriction in the axial direction of the annular portion 6e is performed by the lock-up piston 2.
(Function)
Next, the operation of the torsional vibration reducing device will be described.

  When the engine rotates and its rotational speed reaches a predetermined value, the lockup piston 2 is pressed to the engine side by hydraulic pressure, and the friction lining 2b is pressed and connected to the front cover of the torque converter (not shown). The rotation of the engine is transmitted to the input side member 3 through the lockup piston 2. And it is transmitted from the input side member 3 to the output side member 4 via the 1st spring 11, and is transmitted to the turbine hub and transmission which are not shown in figure.

  Initially, only the first spring 11 is compressed, and when the input side member 3 rotates relative to the output side member 4 by θ relative to a predetermined torque, the second spring 12 is also compressed. At this time, the holding member 6 has an elastic force in the circumferential direction of the first spring 11, a radial centrifugal force due to the weight of the first spring 11, and a radial centrifugal force due to the weight of the connecting portion 6c. Works.

  According to the present invention, since the length of the connecting portion 6c in the circumferential direction is set long to the predetermined value W, the annular portion 6e is reinforced by the long connecting portion 6c. Even when the weight of one spring 11 is increased, the stress generated during rotation can be suppressed.

  According to this invention, since the slit 6d is formed on the inner peripheral side of the connecting portion 6c in the holding member 6, the inertia of the torsional vibration reducing device is reduced. Moreover, since the connection part 6c is separated from the axial center position, the influence of the self-weight centrifugal force can be largely suppressed even if the cutout amount of the slit 6d is small.

  According to the present invention, the connecting portion 6 c of the holding member 6 is formed such that the cross-sectional shape when cut by a cross-section passing through the axial center is a shape in which a plate-like portion is wound along the strand of the first spring 11. Therefore, the area for receiving the end face of the first spring 11 is large. Therefore, the end surface of the first spring 11 can be stably supported, and a retainer need not be provided.

In addition, you may make shapes other than the shape which wound the plate-shaped part along the strand of the spring as a cross-sectional shape when a connection part is cut in the cross section which passes along the axial center of a holding member. Further, the second spring may be accommodated in the first spring without being provided on the inner peripheral side to be a parent-child spring, or the second spring may be eliminated by reducing the maximum allowable torque.

(A) is AA-A sectional view of (b), (b) is a partially broken front view (embodiment) of the torsional vibration reducing device. It is related with the input side member, (a) is BOB sectional drawing of (b), (b) is a front view (embodiment). It relates to the output side member, (a) is a C-C-C cross-sectional view of (b), (b) is a front view (embodiment). It is related with a holding member, (a) is DOD sectional drawing of (b), (b) is a front view (embodiment).

Explanation of symbols

2 ... Lock-up piston (piston)
DESCRIPTION OF SYMBOLS 3 ... Input side member 4 ... Output side member 6 ... Holding member 6c ... Connection part 6d ... Slit (lightening notch part)
6e ... annular portion 11 ... first spring (spring)
11a: Split spring (spring member)
W: Circumferential length
S ... Radial length

Claims (2)

An input side member connected to the crankshaft of the engine via a piston, an output side member provided opposite to the input side member and connected to the transmission, and between the input side member and the output side member At least one pair of springs arranged along a circumferential direction and compressed between the input side member and the output side member and made of a pair of spring members, and an annular portion surrounding the outer peripheral side of the springs In the torsional vibration reduction device having a holding member formed of a coupling portion protruding from the annular portion toward the inner peripheral side and interposed between the pair of spring members,
When the length in the circumferential direction of the connecting portion is W and the length in the radial direction from the base end portion to the distal end portion on the center side of the connecting portion is S, W> S is set.
A torsional vibration reducing device, characterized in that a light-weight cutout portion is formed on an inner peripheral side of an intermediate position in a circumferential direction of the connecting portion . The torsional vibration reducing device according to claim 1,
The torsional vibration is characterized in that the connecting portion is formed in a shape in which a cross-section taken along a cross section passing through the axis of the holding member is formed by winding a plate-like portion along the element wire of the spring. Reduction device.

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